Rotary Working Machine Provided with an Assembly of Working Chambers and Periodically Variable Volume, In Particular a Compressor

ABSTRACT

A rotary working machine is provided. The machine includes an assembly of working chambers with periodically variable volume disposed in a central block defining a stator. The inside surfaces of the stator direct a pendulum motion of one or more blade-type working elements disposed in respective one or more cylindrical sockets of a cylindrical rotator that is disposed within an interior of the camshaft form stator. The rotator is connected to an external prime mover for providing torque thereto. An angle of contact between a front cylindrical surface of the blade-type working elements and the internal curved space of the camshaft form stator defines a working chamber of variable volume, the working chamber of variable volume is connected during rotator revolution correspondingly with an inside pipe of a camshaft and an annular slot that is configured to evacuate compressed gas disposed within the working chamber of variable volume. The outline of a cross-sectional of opening of the camshaft form stator disposed in a vertical plane to with respect to an axis of the cylindrical rotator constitutes the equidistant line to a curve that is described on an immobile plane perpendicular to the axis of the cylindrical rotators by a Radziwill curve. A defined relationship exists between the rotation angle of the cylindrical rotator and the deflection angle of an axis of the working element/

RELATED APPLICATIONS

This application is a continuation-in-part of U.S. application Ser. No.12/326,162, filed on Dec. 2, 2008, which was a continuation of U.S.application Ser. No. 10/592,455, filed on Sep. 7, 2006 and issued asU.S. Pat. No. 7,458,791 on Dec. 2, 2008, which claimed priority from PCTApplication No. PCT/PL2005/000014, filed on Mar. 8, 2005, which claimedpriority from EPO Application No. 04460001.3, filed on Mar. 9, 2004, theentirety of which are each fully incorporated by reference herein.

BACKGROUND

This disclosure relates to a rotary working machine provided with anassembly of working chambers with periodically variable volume, inparticular a compressor.

Since 1908 blade type working machines have been known, employedparticularly as a compressor, consisting of a rotor, eccentricallysupported inside a stationary block and of a set of blades, slidable ingrooves of the rotor. Rotation of the rotor causes the blades moving inand out, which are controlled by an inner surface of the cylindricalblock, thus permitting formation of working chambers with periodicallyvariable volume, enabling intake and compression of a medium.

A disadvantage of blade-type working machines is in energy losses due tofriction of the rotating blades against walls of the cylindrical block,negatively affecting the efficiency and a durability of such machines,particularly at higher speeds.

Since 1927 Pneumaphore type blade compressors have been known, whichwork based upon a principle of oil injection into compressed air,permitting a partial reduction of energy losses and a blade wear. Thisand similar compressor designs have featured blades made of lightaluminum and, since 1964, even lighter plastics. Blade compressors ofsuch designs generally exclude, however, high speed uses, being inconsiderably lower strength of the blades.

U.S. Pat. No. 5,379,736 discloses a combustion engine consisting of anair compressor, a similarly designed exhaust gas decompressor and acombustion chamber positioned between the compressor and thedecompressor. The compressor is provided with two rotating cylinders: anouter cylinder and an inner cylinder, respectively, interconnected andfixed on a common driveshaft, eccentric both in relation to thedriveshaft's axis and between them. An intermediate unit is positionedbetween the rotating cylinders and the intermediate unit is providedwith blades, swiveling on pivots fitted around an axis of the unit,wherein the blades during rotation of the eccentric cylinders takepositions forming, between neighbouring blades and surfaces of thecylinders, chambers with periodically variable volume. A movement of theblades is forced by planetary gears, connecting the driveshaft with thepivots, being axes for the blades' rotation. Furthermore, theintermediate unit is provided with inlet and outlet flanges with valves,controlled by cams fixed on the driveshaft. The blades are rotating inthe same direction as the driveshaft, but at half of the driveshafts'angular speed. Such design reduces considerably the expenditure ofenergy to overcome friction, but a certain amount of energy is consumedto overcome inertia moments of the numerous moving parts of the machine.

German Patent DE 1 551 101 describes a rotary combustion engine,featuring oscillating working elements that are set on pivots in arotating ring and controlled by specially shaped two- or four-lobe cams,located on both sides of the ring. Working elements have, in a section,a shape of triangles with convex sides, the tops of which slide onsurfaces of both cams, forming working chambers with periodicallyvariable volume, causing intake and compression of a medium. During arotation of the driveshaft, each oscillating working element is pressedby a centrifugal force against an inner surface of one cam, and at thesame time tightened in relation to the central cam's outer surface bymeans of sealing strips, pressed against it.

A disadvantage of such engine, prevailing in other rotary engines, is inconsiderable frictional energy losses of numerous working elementsagainst surfaces of cams, and in the difficulty of sealing theextremities of working elements in relation to the cams' workingsurfaces.

Polish Patent PL 109 449 and its German equivalent DE 1526408 disclose arotary combustion engine, featuring an elliptic cylinder, inside whichis moving a system of five pistons, connected by joints to create aclosed chain, while between inner concave surfaces of the pistons andthe elliptic surface of the cylinder, working chambers with periodicallyvariable volume are formed. Pistons, being approximately triangular insection, are interconnected by sealed setting pins, placed in recessesin neighbouring pistons and provided with sealing strips, pressedagainst the elliptic surface of the engine's cylinder. A movement of thepistons is controlled by two rotors or discs, formed by joint-connectedfive segments with axes constituting extensions of axes of setting pins,located on both sides of the engine and transmitting torque to theengine's driveshaft.

A disadvantage of such construction, and other similar designs ofworking machines, in which kinematically connected working elements forma closed chain, is in a presence of variable moments of inertia,increasing friction losses, and thus reducing efficiency of themachines.

International Patent Application WO00/42290 describes a rotarycombustion engine, consisting of an engine block and of a rotor, locatedinside it and featuring four movable pistons, in the form of double-armlevers that oscillate around axes parallel to a central axis of theblock and at the same time revolving together with the rotor. Thepistons are provided with thrust rolls, which during movement along acircumference of the engine block, are driven by a system of cams,consisting of an outer cam and an inner cam. Mating of the thrustelements of the pistons with cam surfaces forces, during the commonrotation, oscillating of the pistons around semicircular projections onthe rotor. The pistons are sealed against each other by means of toothedcontact surfaces, while between their working surfaces and an innercylindrical surface of the engine block are formed chambers withperiodically variable volume, enabling intake and compression of amedium.

A disadvantage of such design is in considerable friction forces,generated between the concave surface of pistons and the semicircularprojections on the rotor, in connection with important mutual pressuresbetween mating surfaces. Considerable frictional losses arise also onthe thrust elements of pistons, driven in a slot between the two cams.

German patent DE 622 554 relates to a working machine with oscillatingpistons, swivel fitted in sockets of a rotor's body. The pistons eachinclude, along with a surface of the rotator's body, working chamberswith periodically variable volume, which are sickle-shaped. Theoscillating pistons are provided with counterweights, swivel on theirpivots in the rotating rotor's body, and slide with their sealing edge,which close the working chamber, in an eccentric relationship to therotor's axis circumference of a stator having circular cross section.Oscillating pistons are provided with counterweights, which position andsize are selected in a way enabling the inertia moment of the piston(caused by a centrifugal force) to be substantially equal to a torquecaused by an acceleration or deceleration of the oscillating piston.

Balancing of torque, resulting from an acceleration and deceleration ofthe piston's oscillation, can be done by appropriate adjustment of theoscillatory piston's counterweight only for one, determined rotationalspeed.

German patent DE 898 697 discloses a working machine that includes withoscillating pistons disposed in sockets on an outer circumference of acylindrical rotator. The pistons are provided with rolls, which move onan inner cam surface of a stator surrounding the rotator and control anoscillating motion of the pistons. A surface of the rotator along with asurface of the stator form working chambers with periodically variablevolume. The oscillating motion of the pistons is limited by stopmembers, which are mounted on an outer surface of the pistons and guidedin grooves, in order to avoid a contact between large surface areas ofthe pistons and the stator. In another embodiment, oscillating pistonsare disposed in cylindrical sockets on an inner outline of an annularrotator surrounding a stator. A cylindrical outer surface of the statoris eccentric in relation to a rotator's axis and forms a guiding surfacefor sealing edges of the pistons. In both embodiments, the oscillatingmotion is forced by a centrifugal force resulting from a displacement ofa mass centre of the pistons in relation to their oscillating axis, orfrom a rolls action, or from a special load.

Disadvantages of that working machine arise from a large motionresistance of the rolls, a motion resistance of the pistons in thesockets and a friction between edges of the pistons and the surface ofthe stator.

BRIEF SUMMARY

It is an object of the invention to provide a rotary working machine,and equipped with a group of working chambers of changeable volume andplaced in the block, in which the rotor rotates with pendulumpistons—working elements, seated in cylindrical sockets and slidingduring rotation in the internal part of the block constituting a specialcurve, which ensures significantly less losses caused by friction, andthus correspondingly increase is the efficiency of the action of themachine.

Experimental and computational research has shown that it is possible toconsiderably limit the energetic losses that result in known rotarymachines with oscillating pistons, of forces acting on individualcomponents of these, by such a correlation of kinematic connectionsystem of the oscillating pistons with distribution of their masses, asto reduce, for any rotation speed of the machine, movements of theseoscillating pistons to resonance oscillations in the field ofcentrifugal force. The resonance character of the oscillating pistons'oscillations enables maintaining the motion by solely overcoming a minorresistance of their replacement in relation to the rotor.

The disclosure provides a rotary working machine that is assembled witha block of which the central part is provided with a stator in the formof a camshaft, the internal surface of which constitutes the surfaceguiding the pendulum motion of the blade type oscillating pistons incylindrical sockets of the cylindrical rotor placed inside this statorin camshaft form and propelled with the aid of a separate engine, inwhich the contact edges of these blade type oscillating pistons areguided by the internal surface of the camshaft form of creating, betweenthis surface, and the intake apertures of the controlling cam andpossibly the surface of the cradle type oscillating piston, workingchambers of changeable volume connected during the rotor rotation to thecorresponding insight pipe of the camshaft and annular slot evacuatingcompressed medium, in which the outline of the cross-section of thecamshaft forms a stator vertical plane to the axis of the rotor thatconstitutes an equally distant line to the curve, as defined by twoparametric equations:

X(φ)=l sin φ+r sin(φ+γ+θ(φ)

Y(φ)=l cos φ+r sin(φ+γ+θ(φ))

where:

φ is a rotation angle of the rotator from a position of minimumpotential energy, that is from a position, in which points O, O1, S areon a single straight line determining an axis OY, as shown in FIG. 5;

X(φ) denotes an abscissa of a position of a vertex point of each of theoscillating pistons of the working element in a co-ordinate systemhaving a centre in the point O being the cylindrical rotator's axis ofrotation, after its rotation through the angle φ;

Y(φ) denotes an ordinate of a position of a vertex point of each of theoscillating pistons of the working element in a co-ordinate systemhaving a centre in the point O being the cylindrical rotator's axis ofrotation, after its rotation through the angle φ;

l is a distance OO1 of the working element oscillation axis from thecylindrical rotator's axis of rotation;

r is a distance of the vertex point from the oscillation axis of theworking element;

γ is a constant angle formed between the axes O1S and O1C, where S is amass centre of the working element; and

θ(φ) is an angle by which the axis O1S deflects during the rotator'smovement through the angle φ,

wherein a relation between the rotation angle φ of the cylindricalrotator and the deflexion angle θ of the axis O1S of the working elementis expressed by an equation:

${\theta (\phi)} = {2{\arcsin \left( {\sin \; \frac{\theta_{0}}{2}\sin \; {\Psi (\phi)}} \right)}}$

where a relation between the angles φ and Ψ is described by tabulatedvalues of elliptic integrals.

Rotary working machine, in particular a compressor according to theinvention, is characterized by a compactness of its design, expressed inthat a ratio of total change of the working chambers' volume (equivalentof a displacement volume) to a volume of inner outline of the machine'smoving part is close to one. Furthermore, an implementation of thecompressor has proven that thanks to the elimination of losses toovercome frictional forces and motion resistance that occur in similarconventional machines, it achieves efficiency in an order of 90%. Insome embodiments, it is necessary for the ratio of the working elementresonance oscillation frequency to the frequency of the rotator'srevolutions to remain, at steady state, constant for all speeds of therotator. In this situation, the machine is relatively highly efficient,independent of the rotator's rotational speed.

Another representative object of the disclosure is provided. The objectincludes rotary working machine provided with an assembly of workingchambers with periodically variable volume, in particular a compressor,placed in block of which the central block 1 in is supplied with acamshaft form stator 4 the inside surface of which constitutes thesurface guiding the pendulum motion of the blade-type working elements10 seated pendulously in cylindrical sockets 22 of the cylindricalrotator 8 placed in the interior of this camshaft form stator 4 andpropelled with the aid of a separate engine, in which the angle ofcontact of these blade-type working elements 10 are conducted throughthe internal curved space of the camshaft form stator 4 creating,between this surface and the front cylindrical surface 31 and possiblythe side cylindrical surface 30 of the blade type working element 10,working chambers of variable volume connected during rotator revolutioncorrespondingly with inside pipe of the camshaft 19 and annular slot 21evacuating compressed medium, in which the outline of the curvedcross-section of opening of the camshaft form stator 4 vertical plane toaxis 17 of the cylindrical rotator 8 constitutes the equidistant line tocurve K_(R) which is described on an immobile plane perpendicular to theaxis of the cylindrical rotators by two parametric equations:

X(φ)=l sin φ+r sin(φ+γ+θ(φ))

Y(φ)=l cos φ+r sin(φ+γ+θ(φ))

where:

φ is a rotation angle of the rotator from a position of minimumpotential energy, that is from a position, in which points O, O₁, S areon a single straight line determining an axis OY in FIG. 4;

X(φ) denotes an abscissa of a position of a vertex point of each of theoscillating pistons of the working element 10 in a co-ordinate systemhaving a centre in the point O being the cylindrical rotator's axis ofrotation, after its rotation through the angle φ;

Y(φ) denotes an ordinate of a position of a vertex point of each of theoscillating pistons of the working element 10 in a co-ordinate systemhaving a centre in the point O being the cylindrical rotator's axis ofrotation, after its rotation through the angle φ;

l is a distance OO₁ of the working element 10 oscillation axis from thecylindrical rotator's axis of rotation;

r is a distance of the vertex point from the oscillation axis of theworking element 10;

γ is a constant angle formed between the axes O₁S and O₁C, where S is amass centre of the working element 10; and

θ(φ) is an angle by which the axis O₁S deflects during the rotator'smovement through the angle φ.

wherein a relation between the rotation angle φ of the cylindricalrotator and the deflexion angle Θ of the axis O₁S of the working element10 is expressed by an equation:

${\theta (\phi)} = {2{\arcsin \left( {\sin \; \frac{\theta_{0}}{2}\sin \; {\Psi (\phi)}} \right)}}$

where a relation between the angles φ and Θ is described by tabulatedvalues of elliptic integrals, marked on this cross-section plane by thevertex point of the blade-type working element 10, moving with regard tothis cylindrical rotator cylinder with the oscillating motion with aresonance frequency during its full rotation at which the moment ofinertia the blade-type working element 10 has a value ensuring itsresonance frequency of own oscillations with regard to cylindricalrotator 8 and it is expressed by the following equation:

$I_{O_{1}} = {\left\lbrack \frac{\pi}{2{vK}_{(\frac{\theta_{0}}{2})}} \right\rbrack^{2} \cdot l \cdot s \cdot m}$

where:

v is a natural number expressing a ratio of frequency of the resonanceoscillation of the working element 10 to a frequency of the rotation ofthe cylindrical rotator, where v=1, 2, 3 . . . ;

l is a distance of the working element 10 oscillation axis from thecylindrical rotator's rotation axis;

s is a distance of a mass centre of the working element 10 from anoscillation axis of the working element 10;

m is a mass of the working element 10;

θ₀ is an angle corresponding to an amplitude of the working element 10oscillation in relation to the rotator.

A machine according to claim 1, characterized in that, its blade-typeworking element 10 as the form of an arched wedge narrowing from sidesurface of side cylindrical surface 30 to the side cylindrical surface30′ through which joining by front cylindrical surface 31, itconstitutes a sector of the cylinder of a radius equal to the radius ofthe cylindrical rotator 8.

Another representative machine is provided wherein the machine ischaracterized in that its blade type-working element 10 is seatedrotationally on axis 23 mounted in projection 29 of cylindrical sockets22 on the cylindrical rotator 8 in this manner, that the frontcylindrical surface 31 of the blade-type working element 10 is coveredby the surface of the cylindrical rotator 8.

Another representative machine is provided wherein the machine ischaracterized in that its cylindrical rotator 8 is supplied with atleast two or more cylindrical sockets 22 of the blade-type workingelements 10, the axes of which are parallel to the axis 17 of rotationof the cylindrical rotator 8.

Another representative machine is provided wherein the machine ischaracterized in that its cylindrical rotator 8 is supplied with fourcylindrical sockets 22 of the blade-type working elements 10, the axesof which are parallel to the axis 17 of rotation of the cylindricalrotator 8.

Another representative machine is provided wherein the machine ischaracterized in that cylindrical sockets 22 are distributed equally onthe circumference of the cylindrical rotator 8.

Another representative machine is provided wherein the machine ischaracterized in that an axis of the inside pipe of the camshaft 19 andannular slot 21 an angle of approx 90 degrees.

Another representative machine is provided wherein the machine ischaracterized in that an axis of controlling nozzle 33 of oil spraycreates with the nearer edge an inlet channel of inside pipe of thecamshaft 19 an angle of approx. 90 degrees.

Another representative machine is provided wherein the machine ischaracterized in that its housing is composed of a central block 1supplied with a camshaft form stator 4 and tightly connected to it withthe aid of a screw 18 the cover block 1 a and the flange of the rearblock 1 b.

Another representative machine is provided wherein the machine ischaracterized in that an inside pipe of the camshaft 19 and annular slot21 have the form of openings executed inside parts of the central block1.

Another representative machine is provided wherein the machine ischaracterized in that the central block 1 and possible cover blockflanges 1 a and rear block 1 b having the view from the front a shapeapproaching a square.

BRIEF DESCRIPTION OF THE DRAWINGS

A rotary working machine according to the disclosure, provided with asystem of working chambers with periodically variable volume,constituting a compressor, will now further be explained with referenceto exemplary embodiments in the accompanying drawings, in which:

FIG. 1 is a side cross-sectional view of a representative compressorequipped with a set of four working chambers, each of which is equippedwith a pendulum seated blade type working element.

FIG. 2 is a cross-sectional view about section A-A of FIG. 1,

FIG. 3 is an exploded view of the compressor of FIG. 1.

FIG. 4 is a Radziwill curve K_(R) constituting the basis of the outlineof the curve controlling the compressor opening according to FIG. 2.

FIG. 5 is a perspective exploded view of a cylindrical socket in rotortogether with pendulum blade type oscillating piston seated in it.

DETAILED DESCRIPTION OF THE DRAWINGS AND THE PRESENTLY PREFERREDEMBODIMENTS

The rotary compressor presented in FIGS. 1-3 is equipped with three parthousing, consisting of central block 1, and cover block 1 a and also ofrear outside block 1 b, also wedged in it on the controlling cam of thecylindrical rotor 8. The block 1 is supplied with camshaft form stator4, of which the transverse cross-section constitutes the furtherreferred to Radziwill curve K_(R) (FIG. 4). Furthermore in the block 1is the inside pipe of the camshaft 19 through which the compressor sucksin the compressed medium and also the annular slot 21 evacuatingcompressed serving to conduct away compressed medium under highpressure. The block 1 is tightly closed on both sides with the aid ofthe flange of the cover block 1 a and the rear block 1 b connected withit with the aid of the screw 18. The cylindrical rotator 8 is wedged onthe controlling cam 5, of which the pivots 13, 14 of the working unitare seated in needle type rolling bearings 15 and 16. The cylindricalrotator 8 furthermore is equipped on its internal surface 24 with fourcylindrical sockets 22 symmetrically placed in its circumference withseated in them on axes 23 of the oscillating blade type-working elements10. Blade type working elements 10 are rotationally seated on axes. Axes23 of working elements 10 are mounted in projections 29 protruding fromrotator interior surface cylindrical sockets 22 (FIG. 5).

Blade type working elements 10 have the form of a two armed lever seatedrotationally in axis 23. This lever is created by two side cylindricalsurfaces 30, 30′ of radius equal or somewhat less than the radius of theinternal surface 24 of the cylindrical socket 22. This lever is alsocreated by front cylindrical surface 31 of radius equal to the radius ofthe cylindrical rotator 8 and rear surface 32 is of the outlet apertureof the controlling cam closing and giving the rotator the form of anarched wedge increasing in the direction of the side cylindrical surface30 of the working element 10. In intersection of side cylindricalsurface 30 and front cylindrical surface 31 of the working element 10 isa set of vertex points C creating the working age of this elementcooperating with the surface of camshaft form stator 4, constituting inthe cross-section the Radziwill curve K_(R). The configuration of eachof the blade type working elements 10 especially its form, dimensionsand material thickness of which it is a security and the distance of thecentre of its axis 23 from the rotation axis 17 of the cylindricalrotator should be so selected in order that the relationship of thefrequency of the blade type working element 10 (for the specified chosenamplitude of oscillations) is the frequency of rotary movement of thecylindrical rotator 8 expressed as a natural number e.g.: 1, 2, 3:

This condition is fulfilled, when the moment of inertia I_(O) ₁ of theblade type-working element 10 with regard to the axis of oscillation O₁fulfils the equation:

$I_{O_{1}} = {\left\lbrack \frac{\pi}{2{vK}_{(\frac{\theta_{0}}{2})}} \right\rbrack^{2} \cdot l \cdot s \cdot m}$

where:

v is a natural number expressing a ratio of frequency of the resonanceoscillation of the working element to a frequency of the rotation of thecylindrical rotator, where v=1, 2, 3 . . . ;

l is a distance of the working element oscillation axis from thecylindrical rotator's rotation axis;

s is a distance of a mass centre of the working element from anoscillation axis of the working element;

m is a mass of the working element; and

θ₀ is an angle corresponding to an amplitude of the working elementoscillation in relation to the rotator.

In order to ensure continual contact of a set of the vertex points C ofblade type working element 10 (creating the contact edge) with thesurface of the camshaft form stator 4 of the block 1 transverse crosssection of this opening (vertically to axis 17 of the cylindricalrotator 8) must constitute the geometric place of points forming theclosed track of movement, which marks on the immobile plane of thevertex point C cross section of the blade type working element 10 movingwith pendulum motion with the movement resonance frequency of the bladetype working element 10 during the time of complete rotation of thecylindrical rotator 8. The geometrical place is the Radziwill curveK_(R) o defined in the system of two parametrical equations:

X(φ)=l sin φ+r sin(φ+γ+θ(φ))

Y(φ)=l cos φ+r sin(φ+γ+θ(φ))

where:

φ is a rotation angle of the rotator from a position of minimumpotential energy, that is from a position, in which points O, O₁, S areon a single straight line determining an axis OY in FIG. 5;

X(φ) denotes an abscissa of a position of a vertex point of each of theoscillating pistons of the working element in a co-ordinate systemhaving a centre in the point O being the cylindrical rotator's axis ofrotation, after its rotation through the angle φ;

Y(φ) denotes an ordinate of a position of a vertex point of each of theoscillating pistons of the working element in a co-ordinate systemhaving a centre in the point O being the cylindrical rotator's axis ofrotation, after its rotation through the angle φ;

l is a distance OO₁ of the working element oscillation axis from thecylindrical rotator's axis of rotation;

r is a distance of the vertex point from the oscillation axis of theworking element;

γ is a constant angle formed between the axes O₁S and O₁C, where S is amass centre of the working element; and

θ(φ) is an angle by which the axis O₁S deflects during the rotator'smovement through the angle φ.

A relationship between the rotation angle φ of the cylindrical rotatorand the deflexion angle Θ of the axis O₁S of the working element isexpressed by an equation:

${\theta (\phi)} = {2{\arcsin \left( {\sin \; \frac{\theta_{0}}{2}\sin \; {\Psi (\phi)}} \right)}}$

where a relation between the angles φ and Θ is described by tabulatedvalues of elliptic integrals.

The above parametric equations describing the Radziwill curve KRconcerns the case of pendulum movement of the blade type-working element10 around axis 23 of the rotation of this element 10 connected immovablywith the cylindrical rotator 8.

The condition for the closure of the vertex movement track point C ofthe blade type working element 10, moving whether pendulum motion withregard to the cylindrical rotator 8 with resonance frequency is thefulfillment of the condition in order that the relationship of theoscillation frequency period of this blade type working element 10 (forthe accepted value of oscillation amplitude) to the frequency ofrotation movement of the cylindrical rotator 8 expressed as a naturalnumber and amounts at the most beneficial to 1 or 2. In actualconstruction of the compressor the movement track in the immobilevertical plane to the axis of the cylindrical rotator 8 (with regard tothe arising abrasion force) does not affect vertex point C, but therounding of the age of contact of the surface 32. The rounding ofsurface 32 constitutes the set of contact points C with the surface ofthe camshaft form stator 4 (equidistant from this vertex point C). Inconnection with this the outline of the cross-section of the camshaftform stator should constitute the equidistant curve with drawn to thecentre from curve KR, ensuring in this manner continuous contact ofpoints of the rounded surface 32 of the appropriate surface points ofthe camshaft form stator 4. In order to reduce friction of the surfacereferred to, the contact surface should be lubricated with an oil jetthrough nozzle of the intake slot of the controlling nozzle 33 on thesurface of the blade type-working element 10. The oil jet shall occurbeneficially during the air suction phase.

In the exemplary construction depicted in FIGS. 1-3, the cylindricalrotator 8 is supplied on its internal surface with four sockets in whichare seated blade type working elements 10. Other numbers of sockets arealso possible within the scope of this disclosure. Providing differingnumbers of sockets would require the corresponding constructionadaptation of the location of the inside pipe of the camshaft and theannular slot evacuating compressed medium within the machine.

The operation of the machine depicted in the figures is discussedherein. Inside the camshaft form stator 4 opening of block 1 of theexternal surface 24 of the cylindrical rotator 8 and the intakeapertures of the front surface 31 of the blade shaped working element 10during its rotation for the working chamber A of variable volume. In thesetting presented on FIG. 2 for its clockwise rotation direction thevolume of chamber A1 increases causing suction of the compressed mediumthrough the inside pipe of the camshaft 19. After rotation of thecylindrical rotator 8 by a central angle of 90 degrees the volume of thechamber increases to the maximal value. Simultaneously in this settingof the rotator, this chamber is closed by the vertex points C ofadjacent working elements 10. During further rotation of the cylindricalrotator 8 follows the reduction of the volume of chamber A3, andsimultaneously oil jet through oil jet nozzle 33. Supplied workingchamber to A3 the oil fulfils a triple function, because it lubricatesthe rear surface 32 of the blade type working element 10 creating acurved opening from the surface of camshaft form stator 4 a wedge of oilreducing friction, simultaneously sealing these surfaces and alsoconducting away heat being the result of the compression process toinvisible coolers. In this last movement phase, corresponding to thefurther rotation of the rotator by a following angle of next 90 degreesfollows the opening the annular slot 21 evacuating compressed medium andconducting away the compressed medium to peripheral appliances of thecompressor.

Experimental operation of a prototype compressor built according to thedesign disclosed herein confirmed that its optimal operation compressioncorresponds to a large extent of rotation frequencies of the cylindricalrotator 8. But after exceeding a defining boundary value of thesefrequencies further increase of rotation speed causes a proportionalgrowth of compressor output. For example driving the compressor with anengine of 3 kW power a working pressure of 11×105 Pa and output ofapprox. 300 dm3/min. was obtained.

It will therefore be understood by those skilled in the art that thepresent is not limited to the embodiment shown and that manymodifications are possible without departing from the scope of thepresent invention as defined in the appending claims.

1. A rotary working machine comprising: an assembly of working chamberswith periodically variable volume disposed in a central block thatcomprises a camshaft form stator, an inside surface of the camshaft formstator defines a surface guiding pendulum motion of one or moreblade-type working elements disposed pendulously in respective one ormore cylindrical sockets of a cylindrical rotator that is disposedwithin an interior of the camshaft form stator, the rotator is connectedto an external prime mover for providing torque thereto, an angle ofcontact between a front cylindrical surface of the blade-type workingelements and the internal curved space of the camshaft form statordefines a working chamber of variable volume, the working chamber ofvariable volume is connected during rotator revolution correspondinglywith an inside pipe of a camshaft and an annular slot that is configuredto evacuate compressed gas disposed within the working chamber ofvariable volume, wherein an outline of a cross-sectional of opening ofthe camshaft form stator disposed in a vertical plane to with respect toan axis of the cylindrical rotator constitutes the equidistant line to acurve that is described on an immobile plane perpendicular to the axisof the cylindrical rotators by two parametric equations:X(φ)=l sin φ+r sin(φ+γ+θ(φ))Y(φ)=l cos φ+r sin(φ+γ+θ(φ)), and wherein a relationship between therotation angle φ of the cylindrical rotator and the deflection angle Θof the axis O₁S of the working element is expressed by an equation:${{\theta (\phi)} = {2{\arcsin \left( {\sin \; \frac{\theta_{0}}{2}\sin \; {\Psi (\phi)}} \right)}}},$wherein a relationship between the angles φ and Θ is described bytabulated values of elliptic integrals, marked on this cross-sectionplane by the vertex point of the working element. moving with regard tothis cylindrical rotator cylinder with the oscillating motion with aresonance frequency during its full rotation at which the moment ofinertia the blade-type working element has a value ensuring itsresonance frequency of own oscillations with regard to cylindricalrotator and it is expressed by the following equation:$I_{O_{1}} = {\left\lbrack \frac{\pi}{2{vK}_{(\frac{\theta_{0}}{2})}} \right\rbrack^{2} \cdot l \cdot s \cdot {m.}}$2. The machine of claim 1, wherein the working element is an archedwedge that narrows from a side surface of a first side surface to anopposite second side surface, with the first and second side surfacesjoined by a front cylindrical surface that forms a sector of thecylinder with a radius substantially the same as a radius of thecylindrical rotator.
 3. The machine of claim 2, wherein the blade typeworking element is seated rotationally on an axis mounted within acylindrical socket disposed upon the cylindrical rotator, wherein thefront cylindrical surface of the blade type working element is coveredby the surface of the cylindrical rotator.
 4. The machine of claim 1,wherein the cylindrical rotator comprises two or more sockets and bladetype working elements, the axes of which are each substantially parallelto an axis of rotation of the cylindrical rotator.
 5. The machine ofclaim 4, wherein the cylindrical rotator comprises four cylindricalsockets and blade type working elements.
 6. The machine of claim 4,wherein the cylindrical sockets are disposed upon the cylindricalrotator with equal spacing between each neighbouring cylindrical socket.7. The machine of claim 5, wherein an axis through the inside pipe ofthe camshaft is disposed approximately perpendicularly to an axisthrough the angular slot.
 8. The machine of claim 5, wherein an axisthrough a controlling nozzle for spray is disposed approximatelyperpendicularly to an axis through the inside pipe of the camshaft. 9.The machine of claim 1, wherein the housing is fixed to a cover blankand a flange of a rear block.
 10. The machine of claim 9, wherein theinside pipe of the camshaft and the annular slot each comprise openingsdefined within the central block.
 11. The machine of claim 1, whereinthe central block defines a substantially square shape.
 12. The machineof claim 11, wherein t central block, a cover block, and a rear blockeach define the substantially square shape.
 13. The machine of claim 1,wherein the working chambers of variable volume further are defined bythe first side cylindrical surface of the blade type working element.